KR19980081081A - Shroud Type Compressor - Google Patents

Abstract

Provided is a scroll compressor that prevents longitudinal vibration due to a difference in plan view of the seal bearing or a micro step in the oil supply groove. By forming an oil supply groove communicating with the oil space on the thrust surface to which the seal bearing is slidingly connected, it is possible to secure a substantial thrust region of the thrust surface to which the seal bearing is substantially interlocked when the drive shaft is inclined. Because of this, the shaft can be prevented from moving up and down due to the micro step or the flatness of the surface of the seal bearing.

Description

Shroud Type Compressor

The present invention is a compressor used as a refrigerant compressor of a refrigerator and an air conditioner, and has a fixed scroll formed in a spiral shape and a swinging scroll for engaging with the fixed scroll to form a compression chamber. The present invention relates to a scroll compressor that compresses a refrigerant by changing a volume of the compression chamber while causing a rotational motion that does not rotate relative to it.

The scroll compressor disclosed in Japanese Patent Laid-Open No. 7-97995 includes a drive shaft rotating by a drive means, an eccentric shaft extending in the axial direction from the lower end surface of the drive shaft, and a rocking scroll member mounted on the eccentric shaft; The oscillating scroll member has a fixed scroll member to form a compression chamber by engaging with the block, while maintaining the drive shaft to be free to rotate and at the same time the fixed scroll member is fixed, the oil reservoir is formed on the top of the block At the same time, the oil space formed near the lower end of the main bearing and the swing space in which the oscillating scroll member pivots are blocked by pressure as a seal bearing. For this reason, the lubricating oil forms the lubricating oil path which a lubricating oil moves to a suction side in an oil storage cylinder by the differential pressure of a high pressure side and a low pressure side.

Further, the seal bearing disclosed in the above example is such that the oil bearing and the swinging space are pressurefully interrupted while maintaining the drive shaft to be free to rotate in the axial direction. Disclosed is a seal washer interposed between and an elastic member provided outside the lower end side surface of the seal bearing. For this reason, it is made to absorb the inadequate condition in the case where a drive shaft is inclined as an elastic member. Also disclosed is a seal reinforcement.

Further, it is disclosed that an annular groove is formed on the upper side of the seal bearing, and a plurality of radial grooves communicating with the annular groove and the outer circumferential side are formed. As a result, high pressure lubricating oil in the oil space is supplied to the spinning groove, whereby the pressing force in the axial direction upward of the drive shaft can be increased.

However, in the compressor of the above-described configuration, when the drive shaft (shaft) is inclined and assembled due to unbalance of the assembly, the linking surface between the shaft and the seal bearing, or the linking surface between the shaft and the seal bearing, or the shaft and the seal bearing, In the interface between the seal washer and the seal bearing interposed therebetween, there is a non-rust region which is substantially in an upright state with the actual thrust region which is substantially connected. For this reason, in the case of a position where the oil supply groove occupies a large portion in the real thrust region, the thrust region in a case where the proportion of the oil supply groove in the real thrust region in the thrust region is small. Since the amount of deformation is small and the shaft is not lowered, the shaft vibrates longitudinally by the number of the shaft and the oil supply groove by one rotation of the shaft, which is a problem in the noise vibration surface. Moreover, it is confirmed that this inadequate occurrence also arises by the difference of the top view of the said seal bearing.

It is therefore an object of the present invention to provide a scroll compressor that prevents longitudinal vibration caused by a difference in plan view of the seal bearing and a small step of the oil supply groove.

Accordingly, the present invention provides a sealed case in which the inlet pipe and the outlet pipe are mounted, a drive means disposed in the sealed case, a drive shaft extending from the drive means, and a main bearing for rotatably supporting one end of the drive shaft. And a block fixed to the sealed case, an eccentric shaft projecting eccentrically from one end surface in the axial direction of the drive shaft, and the eccentric shaft is freely mounted, and a swinging screw spirally extending in the axial direction from the opposite side thereof. It has a swinging scroll member and a fixed scroll to engage with the swinging scroll to form a compression chamber, the fixing screw is fixed to the block by sandwiching the swinging scroll member to swing freely between the blocks; It is arrange | positioned between the roll member, the one end surface of the said drive shaft, and the said block, and the one end surface of the said drive shaft is free to slide. In the scroll compressor having a seal bearing portion for pressure-blocking the turning space on the swinging scroll side and the oil space on the main bearing side in communication with the oil reservoir formed on the block. And a thrust surface slidingly connected to the seal bearing, and an oil supply port communicating with the oil space.

Therefore, according to the present invention, an oil supply groove communicating with the oil space is formed on the thrust surface to which the seal bearing is slidingly connected, so that the seal surface of the thrust surface to which the seal bearing is substantially interlocked when the driving shaft is inclined. Since the streak area can be secured constantly, the up and down movement of the drive shaft can be prevented, and thus the above problems can be achieved.

Moreover, the said thrust surface is the side surface of the seal bearing side of the seal washer arrange | positioned between the said seal bearing and the said drive shaft, The said thrust surface is the cross section of the drive shaft with which the said seal bearing cooperates.

In the present invention, the oil supply groove is preferably composed of an annular groove formed in an annular contact surface with the seal bearing and a plurality of spinning grooves passing through the annular groove and the oil space. .

BRIEF DESCRIPTION OF THE DRAWINGS The schematic sectional drawing of the scroll compressor which concerns on embodiment of this invention.

2 is an enlarged partial sectional view of a scroll compressor according to an embodiment of the present invention.

3 is an exploded perspective view showing the configuration of the vicinity of a seal bearing according to the first embodiment of the present invention; And

4 is an exploded perspective view showing the configuration of a seal bearing vicinity according to a second embodiment of the present invention.

* Explanation of symbols for the main parts of the drawings

1: Shroud type compressor 2: Closed case

3: inlet pipe 4: cylindrical case

5: outlet pipe 6: power supply terminal

7A: Upper part 7B: Lower part

8 drive unit 9 compression unit

10: woman coil 11: stator

12: rotor 13: drive shaft (shaft)

14: retaining plate 15: bearing

16 block 17 through hole

18: main bearing 19: balance weight

20: spiral groove (screw groove) 21: eccentric shaft

24: cover 25: parts

26: refrigerant passage 27: oil defrosting

28: high pressure space 29: hook shape

30: rocking scroll member 40: compression chamber

50: fixed scroll member 53: discharge hole

60: discharge space 80: thrust bearing

82: sealing

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described by drawing.

In the scroll compressor 1 shown in Figs. 1 and 2, the sealed case 2 closes the cylindrical case 4 in which the inlet pipe 3 is installed and the upper opening end of the cylindrical case 4. The upper part 7A on which the outlet pipe 5 and the power supply terminal 6 are mounted at the same time as the new box, and the lower part 7B closing the lower opening end of the cylindrical case 4. ), The drive unit 8 and the compression unit 9 are housed in the sealed case 2.

The drive unit 8 is fixed to the inner circumferential side of the sealed case 2 and at the same time, a plurality of magnetic poles are applied to the stator 11 and the surface opposed to the stator 11, on which the excitation coil 10 is wound. The rotor is composed of a rotor 12 equipped with a permanent magnet and a drive shaft (shaft) 13 to which the rotor 12 is fixed, and the stator 11 is excited by the excitation coil 10 so that the rotor is excited. A rotor magnetic field is generated with respect to 12, and the rotor 12 is rotated.

The shaft 13 which connects the drive part 8 and the compression part 9 mentioned below is hold | maintained freely by the bearing 15 attached to the holding plate 14, and the lower part is It is held so as to be free to rotate by the main bearing 18 mounted in the through hole 17 of the block 16 described below. The shaft 13 is provided with a balance weight 19 for maintaining the rotational balance of the swinging scroll member 30 described below. In addition, the shaft 13 is formed with a threaded groove 20 formed to be inclined in the rotational direction on the interlocking sliding surface with the main bearing 18 to lubricate the interlocking sliding portion, and the shaft ( At the end portion in the axial direction of 13, an eccentric shaft 21 which is eccentrically protruded from the axial center of the shaft 13 and protrudes in the axial direction is formed, and a hole and an eccentric shaft 21 formed near the distal end of the threaded groove 20 are formed. The oil introduction hole 23 which communicates with the hole formed in the cross section of () is formed.

The compression unit 9 swings to perform a rotational movement (hereinafter, referred to as a rocking movement) in which rotation is prevented according to the rotation of the block 16 and the shaft 13 fixed to the inner side surface of the sealed case 2. It is comprised by the scroll member 30 and the fixed scroll member 50 which meshes with the said swing scroll member 30, and forms the compression chamber 40. As shown in FIG.

The block 16 is provided with the through hole 17 penetrating the inside in the axial direction, and maintains the shaft 13 freely through the main bearing 18. In addition, the upper surface of the block 16 is provided with a cover 24 surrounding the rotation range of the balance weight 19, and a coolant passage 26 is formed in each portion 25 of the cover 24. . In addition, the upper portion of the block 16 is formed with an oil reservoir 27, and further, the oil reservoir 27 is a high pressure space 28 communicating with the outlet pipe 5. The reservoir 27 has an oil passage 72 and an oil passage 73 formed by the shaft 13, the block 16, the lower end of the main bearing 18 and the seal bearing 80 described below. It is communicated through. In addition, one end of the oil introduction hole 23 and the threaded groove 20 is opened in the oil space 72.

In addition, the lower surface of the block 16 has a block-side old wall groove 70 in which the hook-shaped portion 29A on the block side of the old wall ring 29 which prevents the rotation of the swinging scroll member 30 described below is engaged. A coolant passage hole 71 is formed in the vicinity of the side of the block 16 to communicate with the coolant passage 26.

On the block side surface of the swinging scroll member 30, a swinging bearing 31 into which the eccentric shaft 21 is inserted, and a hook-shaped portion 29B on the swinging scroll side of the old dam ring 29 are engaged. The swinging screw side old wall groove 32 is formed.

In addition, since the eccentric shaft 21 is inserted into the swing bearing 31, a bearing space 33 is formed inside the swing bearing 31. In addition, a swinging scroll 34 formed in a spiral shape is formed on the side of the fixed scroll side of the swinging scroll member 30.

The fixed scroll member 50 is engaged with the swinging scroll 34 of the swinging scroll member 30 to form a fixed scroll 51 constituting the compression chamber 40. Further, the fixed scroll member 50 is formed near the outer circumferential side thereof. The inlet pipe 3 is in communication with the inlet space 52 to be the suction side of the compression chamber 40 is formed, and the discharge hole 53 to be the discharge side of the compression chamber 40 is formed in the center portion. do. In the vicinity of the intermediate position of the compression chamber 40, a bypass passage 54 is formed in which the compression chamber 40 communicates with the discharge space 60.

The holding plate for holding and holding the relief valve 62 for opening and closing the bypass passage 54 while holding the valve 61 in the opening of the discharge hole 53 of the fixed scroll member 50. (63) is screwed in. In addition, a discharge space 60 formed by the cover 74 is formed at the discharge side of the discharge hole 53. The discharge space 60 communicates with the high pressure space 28 through the refrigerant passage hole 71 and the refrigerant passage 26.

In the scroll compressor 1 having the above-described configuration, as the shaft 13 rotates, the swinging scroll member 30 oscillates with respect to the fixed scroll member 50, and thus the compression chamber 40 is rotated. By changing the volume of the refrigerant is sucked in the suction space 52 is to discharge from the discharge hole (53).

In addition, the lubricating oil contained in the oil reservoir 27 raises the threaded groove 20 in the oil space 72 and lubricates the sliding interface between the main bearing 18 and the shaft 13 to hold the oil reservoir. A bearing space (1) is passed through the oil introduction hole (23) in the oil space (72) along the first lubrication route returning to (27), or by the differential pressure of the high pressure space (28) and the suction space (52) on the other side. 33), while lubricating the interlocking sliding surfaces of the eccentric shaft (21) and the swinging bearing (31), and swinging in the swinging space (74), which is the swinging range of the swinging bearing (31) of the swinging scroll member. Lubricating the thrust guide 76, which is a sliding interface between the 30 and the block 16, and lubricating the Olddam ring 29, the Oldham grooves 32, 70, into the suction space 52 It passes through the second lubrication route. In addition, the lubricating oil that reaches the suction space 52 in the second lubrication route is sucked together with the refrigerant to contact the sealing surface of the compression chamber 40 and the contact surface of the swinging scroll member 30 and the fixed scroll member 50. Lubrication is carried out to reach the high pressure space 28 together with the refrigerant, where the oil is separated and returned to the oil reservoir 27.

In the second lubrication route, the oil space 72 and the swing space 75 are pressure-closed by the seal bearing portion 80, and the pressure difference between the high pressure space 28 and the suction space 52 is reduced. The lubricating oil is reliably flowed from the oil space 72 to the bearing space 33 via the oil introduction hole 23, and the seal bearing portion 80 supports the shaft 13 in the axial direction. Has a role.

This seal bearing part 80 is a seal washer 82 formed in one phase as shown in FIG. 3, and the seal washer 81 in which the seal bearing 82 and the drive shaft 13 are disposed between the end portions 13A. ) And an elastic ring 83 provided between the seal bearing 82 and the block 16. The seal bearing 82 is annularly formed by cast iron or the like, and has a side surface having a predetermined surface roughness and a stepped portion 82A to which the elastic ring 83 described below is mounted.

In addition, the elastic ring 83 is formed of a synthetic resin such as Teflon and is adapted to absorb the grooves to be inclined to seal the seal bearing portion 80.

In addition, a plurality of radially formed annular grooves 84 formed in an annular shape in a linking surface of the seal washer 81 with the seal bearings 82 so as to communicate with the annular grooves 84 and the oil space 72. An oil supply groove formed in the spinning groove 85 is formed. Thus, since the high pressure lubricating oil reaching the oil space 72 reaches the annular groove 84 in the spinning groove 85, the axial direction in which the high pressure space 28 is caught by the shaft 13 by pressure. It is possible to kill the force of, so that the smooth rotation of the shaft 13 can be maintained.

In addition, when the shaft 13 is inclined on the seal bearing side due to unevenness during assembly, the sliding interface between the seal washer 81 and the seal bearing 82 is substantially mutually connected with the real thrust region. Since non-rust regions are formed in non-contact with each other, conventionally, a slight difference between the oil supply grooves occupying the actual real regions that change due to the rotation of the shaft causes vertical movement of the shaft 13, causing noise and vibration. In the present invention, the oil supply grooves (annular grooves 84 and the radial grooves 85) are formed on the side of the seal washer 81 which rotates in cooperation with the shaft 13 as described above. Since the actual thrust area on the side can be secured at a predetermined position, the micro-step of the oil supply groove or the sliding surface of the seal bearing are not changed in the difference in plan view, and thus the shaft It is possible to prevent the up and down movement.

In the first embodiment, oil supply grooves 84 and 85 are formed in the seal washer 81 in which the seal bearing 82 slides, but as shown in FIG. 4, the seal washer 81 is shown. In a scrawl compressor in which the seal bearing 82 is in direct contact with the end face 13A of the shaft 13 without using), the oil is applied to the shaft end face 13A in which the seal bearing 82 is directly connected and engaged. Even if the supply grooves 84 and 85 are formed, the same effects as in the above-described first embodiment can be obtained.

As described above, according to the present invention, an oil supply groove is formed in a seal washer in which the seal bearing slides in a seal bearing portion that seals between the oil space and the swing space and supports the shaft in the axial direction. Therefore, even when the shaft is inclined, the sliding connection portion of the seal washer with the oil supply groove can be kept at a predetermined position, thereby preventing the vertical movement of the shaft due to the micro step of the seal bearing and the difference in the flatness of the compressor. Low noise and low vibration can be achieved.

Claims (6)

In scrollable compressors: An airtight case in which the inlet pipe and the outlet pipe are mounted; Drive means disposed in the sealed case; A drive shaft extending from the drive means; A main bearing supporting one end of the drive shaft so as to be free to rotate, the block being fixed to the sealed case; An eccentric shaft which protrudes eccentrically from one end surface in the axial direction of the drive shaft; A swinging scroll member which is mounted so that the eccentric shaft is free to rotate and has a swinging scroll extending in a axial direction on an opposite side thereof; A fixed scroll member having a fixed scroll engaged with the swing scroll to form a compression chamber, the fixed scroll member being secured to the block by swinging the swing scroll member freely between the block; A turning space disposed between the one end surface of the drive shaft and the block, the swing space being on the oscillating scroll side while maintaining the one end surface of the drive shaft to be free to slide; A seal bearing for pressurearily blocking the oil space on the main bearing side in communication with the oil reservoir formed on the block; And And the seal bearing is formed on a thrust surface in sliding engagement with an oil supply groove communicating with the oil space. 2. The scroll compressor of claim 1, wherein the thrust surface has a side of a seal bearing side of a seal washer disposed between the seal bearing and the drive shaft. 2. The scroll compressor of claim 1, wherein the thrust surface is a cross section of a drive shaft to which the seal bearing is linked. The oil supply groove according to claim 1, wherein the oil supply groove is composed of an annular groove formed annularly in the linking contact surface with the seal bearing, and a plurality of spinning grooves communicating the annular groove with the oil space. Roll type compressor. 3. The oil supply groove according to claim 2, wherein the oil supply groove is composed of an annular groove formed annularly in the linking contact surface with the seal bearing, and a plurality of spinning grooves communicating the annular groove with the oil space. Roll type compressor. 4. The oil supply groove according to claim 3, wherein the oil supply groove is formed by an annular groove formed in an annular contact surface with the seal bearing and a plurality of spinning grooves communicating the annular groove with the oil space. Shroud type compressor.